EP1655515A1 - Power-split hydromechanical transmission with summing transmission means - Google Patents

Power-split hydromechanical transmission with summing transmission means Download PDF

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Publication number
EP1655515A1
EP1655515A1 EP05110321A EP05110321A EP1655515A1 EP 1655515 A1 EP1655515 A1 EP 1655515A1 EP 05110321 A EP05110321 A EP 05110321A EP 05110321 A EP05110321 A EP 05110321A EP 1655515 A1 EP1655515 A1 EP 1655515A1
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EP
European Patent Office
Prior art keywords
gear
stage
transmission
hydrostatic transmission
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05110321A
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German (de)
French (fr)
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EP1655515B1 (en
Inventor
Andreas Meise
Bernhard Langenbeck
Steffen Reiblein
Frank Nagel
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Lohmann and Stolterfoht GmbH
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Lohmann and Stolterfoht GmbH
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Application filed by Lohmann and Stolterfoht GmbH filed Critical Lohmann and Stolterfoht GmbH
Priority to EP06121775A priority Critical patent/EP1734286B1/en
Priority to PL06121775T priority patent/PL1734286T3/en
Publication of EP1655515A1 publication Critical patent/EP1655515A1/en
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Publication of EP1655515B1 publication Critical patent/EP1655515B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges

Definitions

  • the present invention relates to a transmission arrangement, in particular for a drive of a vehicle, with a hydrostatic transmission, which is followed by at least one planetary stage, wherein the coupling of the planetary gear to the hydrostatic transmission via intermediate transmission means for speed superposition takes place within the planetary stage.
  • a hydrostatic transmission consisting of a variable speed hydraulic pump and a downstream hydraulic motor provides a continuously variable output speed to the wheels or tracks of the vehicle.
  • the speed can be varied continuously by controlling the displacement of the variable displacement hydraulic pump.
  • the engine torque is split between the hydrostatic transmission and a mechanical transmission coupled thereto.
  • the mechanical transmission in the form of at least one planetary gear stage, has a number of gear ranges corresponding to the different operating speeds of the wheel drive.
  • the transmission assembly includes a hydrostatic transmission coupled to a mechanical transmission to select a first range of travel and a second range of travel.
  • a control device carries out a switching operation from the first transmission region provided for this purpose to the second transmission region.
  • the invention includes the technical teaching that corresponding to a first driving range, the sun gear of the single planetary stage via a first clutch with a ring gear of the planetary stage is in operative connection, so that the output speed of the planetary stage depends linearly on the output speed of the hydrostatic transmission, and that further accordingly a second driving range, the ring gear is in operative connection with the hydrostatic transmission, wherein at the same time the sun gear via a second clutch with a Transmission input shaft is in operative connection, so that superimpose the rotational speeds of the ring gear and sun gear, and that the first clutch via a gear stage with the ring gear of the planetary stage is in operative connection, and that the ring gear via a gear stage with the hydrostatic transmission is in operative connection, wherein at least a gear stage has a spur gear rigidly mounted on a shaft and the shaft is driven by the hydrostatic transmission to connect the ring gear and the sun gear of the planetary gear stage in the first driving range.
  • the advantage of the gear arrangement according to the invention is in particular that hereby a high transmission ratio is possible by changing the mode of operation via two clutches, whereby two complementary driving ranges are provided for the forward travel of a vehicle. With the addition of a further clutch, two driving ranges for the reverse travel of the vehicle can be provided.
  • the relatively low cost of mechanical components results from the fact that only one planetary stage is used as an overlay stage. In the first driving range, the ring gear and the sun gear of the planetary stage are connected to each other via the clutch. The drive takes place starting from the transmission input shaft via the hydrostatic transmission in the planetary stage, the planetary web forms the output.
  • the drive is power-split on the one hand directly mechanically via the second clutch to the sun gear of the planetary stage and on the other hand via the hydrostatic transmission to the ring gear of the planetary stage.
  • the output continues via the planet web.
  • the first clutch is open in this case.
  • both gear stages each have a rigidly arranged on a common shaft spur gear, and that the shaft is driven by the hydrostatic transmission. This results in a particularly component-saving arrangement.
  • the gear stage may have a spur gear rigidly mounted on a shaft, and the shaft may be driven by the hydrostatic transmission, said spur gear meshing with an externally toothed ring gear of the downstream gear stage.
  • the switching between the first driving range and the second driving range is effected by a mutual actuation of the two clutches via a central control unit, which at the same time also controls the hydrostatic transmission in accordance with the driving intention.
  • the gear arrangement according to the invention may contain different gear stages for the purpose of speed adaptation.
  • the transmission input shaft drives the hydrostatic transmission preferably via an intermediate gear stage.
  • the first clutch can be in operative connection with the ring gear of the planetary stage via an additional gear stage, ie indirectly.
  • the ring gear is also operatively connected to the hydrostatic transmission via an intermediate gear stage.
  • At least one further additional clutch is arranged between the transmission input shaft and the sun gear of the planetary stage in order to enable at least one second driving range even in reverse.
  • this additional clutch is also operatively connected to the transmission input shaft via an associated gear stage having a direction-changing intermediate gear.
  • the gear arrangement follows the force flow from an input-side gear input shaft 1, which is driven by a motor (not shown).
  • the transmission input shaft 1 is connected downstream of a hydrostatic transmission 2.
  • the hydrostatic transmission 2 consists of an adjustable hydraulic pump 2 a, which is hydrostatically coupled to an adjustable hydraulic motor 2 b.
  • a planetary stage 3 is coupled.
  • the end coupling 4 is in communication with the sun gear 3b of the planetary stage 3.
  • the planet carrier 3c of the planetary stage 3 forms the output of the gear assembly.
  • the power flow is in a first driving range of the transmission input shaft 1 via an input side gear 7 on the drive shaft of the variable displacement 2a of the hydrostatic transmission 2.
  • the output shaft of the hydrostatic motor 2b of the hydrostatic transmission 2 is connected via downstream gear stages 8 and 9 in operative connection with the ring gear 3a the planetary stage 3 and also with the clutch 4 of the parallel power flow.
  • By closing the clutch 4 in the first driving range ring gear 3a and 3b of the planetary planetary gear 3 via the gear stages 8 and 9 are additionally interconnected, whereby the number of degrees of freedom of the planetary stage 3 is reduced so that the output speed of the planetary gear 3c directly from the output speed of Hydraulic motor 2b depends.
  • variable displacement pump 2a in the opposite direction means another direction of rotation on the hydraulic motor 2b and thus a reverse drive of the vehicle.
  • the ratios of the gear stages 7 to 10 and the planetary stage 3 are coordinated such that at maximum speed of the variable hydraulic motor 2b, the sun gear 3b and the shaft 6 of the parallel power flow has the same speed.
  • the first clutch 4 is opened and the second clutch 5 is closed by means of a - not shown here - control unit. Accordingly, the sun gear 3b of the planetary stage 3 rotates in a constant speed in the same direction as the planetary gear 3c while the ring gear 3a rotates at the maximum rotational speed in the opposite direction.
  • a further clutch 5b is introduced with associated gear stage 10b.
  • the gear stage 10b includes an intermediate gear 11 for changing the direction of rotation.
  • Figure 3 has - in contrast to the former embodiment - only designed as a spur gear 8 a gear on the shaft rigidly arranged spur gear, which is driven by the hydr660 + 160ostatic transmission 2.
  • the said spur gear in turn meshes with an externally toothed ring gear 9a of the downstream gear stage 9, which is here a planetary gear.
  • the clutch 4 is used to fix the planetary land 9c of gear stage 9.
  • the sun gears 3b and 9b of the gear stages 3 and 9 are arranged on a common shaft which is fixable with the clutch 5.
  • the gear stage 9 downstream planetary stage 3 is also driven by a common ring gear 9a and 3a.
  • the output at the planetary stage 3 also takes place via the planetary land 3c.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Control Of Transmission Device (AREA)
  • Retarders (AREA)
  • Motor Power Transmission Devices (AREA)
  • Arrangement Of Transmissions (AREA)
  • Control Of Eletrric Generators (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)

Abstract

A sun gear (3b) is in effective interaction with a gearbox input shaft (1) via a second coupling (5) so that as a consequence of power distribution, the ring and sun gear speeds overlap and in that the first coupling (4) is in effective interaction with the ring gear (3a) of the planetary stage (3). A gearbox stage (8) has a spur gear mounted on a shaft driven by a hydrostatic gearbox (2) to connect the ring and sun gears of the planetary stage.

Description

Die vorliegende Erfindung betrifft eine Getriebeanordnung, insbesondere für einen Antrieb eines Fahrzeuges, mit einem hydrostatischen Getriebe, dem mindestens eine Planetenstufe nachgeschaltet ist, wobei die Ankopplung der Planetenstufe an das hydrostatische Getriebe über zwischengeschaltete Getriebemittel zur Drehzahlüberlagerung innerhalb der Planetenstufe erfolgt.The present invention relates to a transmission arrangement, in particular for a drive of a vehicle, with a hydrostatic transmission, which is followed by at least one planetary stage, wherein the coupling of the planetary gear to the hydrostatic transmission via intermediate transmission means for speed superposition takes place within the planetary stage.

Das Einsatzgebiet derartiger Getriebeanordnungen erstreckt sich vornehmlich auf Fahrzeuge, insbesondere Erdbearbeitungsfahrzeuge und dergleichen. Die spezielle Getriebeanordnung dient als kontinuierlich variables Getriebe zum Antrieb solcher Fahrzeuge.The field of application of such gear arrangements extends primarily to vehicles, in particular Erdbearbeitungsfahrzeuge and the like. The special gear arrangement serves as a continuously variable transmission for driving such vehicles.

Aus dem allgemeinen Stand der Technik gehen gattungsgemäße Getriebeanordnungen hervor, bei denen die mechanische Leistungsübertragung mit einem stufenlos verstellbaren hydrostatischen Getriebe kombiniert wird. Zweck dieser Getriebeanordnung ist es, den Wandlungsbereich eines hydrostatischen Fahrantriebs zu vergrößern und ein Schalten ohne Zugkraftunterbrechung zu ermöglichen. Typischerweise liefert ein hydrostatisches Getriebe, das aus einer Hydraulikpumpe mit variabler Drehzahl und einem nachgeschalteten Hydraulikmotor besteht, eine kontinuierlich variable Ausgangsdrehzahl an die Räder oder Raupen des Fahrzeuges. Insbesondere kann die Drehzahl kontinuierlich durch Steuerung der Verdrängung der verstellbaren Hydraulikpumpe variiert werden. Um nun einen weiten Fahrbereich abzudecken, wird das Motordrehmoment zwischen dem hydrostatischen Getriebe und einem hiermit gekoppelten mechanischen Getriebe aufgeteilt. Das mechanische Getriebe, in Form mindestens einer Planetengetriebestufe, hat eine Anzahl von Getriebebereichen entsprechend den unterschiedlichen Betriebsdrehzahlen des Radantriebs. Die Kombination des hydrostatischen Getriebes mit dem mechanischen Getriebe ermöglicht es, ein kontinuierlich variables Getriebe bereitzustellen, das über einen weiteren Bereich von Drehzahlen arbeitet, als es unter Verwendung eines hydrostatischen Getriebes alleine möglich ist.From the general state of the art generic gear arrangements emerge, in which the mechanical power transmission is combined with a continuously variable hydrostatic transmission. The purpose of this gear arrangement is to increase the conversion range of a hydrostatic drive and to enable switching without interruption of traction. Typically, a hydrostatic transmission consisting of a variable speed hydraulic pump and a downstream hydraulic motor provides a continuously variable output speed to the wheels or tracks of the vehicle. In particular, the speed can be varied continuously by controlling the displacement of the variable displacement hydraulic pump. In order to cover a wide driving range, the engine torque is split between the hydrostatic transmission and a mechanical transmission coupled thereto. The mechanical transmission, in the form of at least one planetary gear stage, has a number of gear ranges corresponding to the different operating speeds of the wheel drive. The combination of the hydrostatic transmission with the mechanical transmission makes it possible to provide a continuously variable transmission that operates over a wider range of speeds than is possible using a hydrostatic transmission alone.

Aus der DE 101 44 943 A1 geht eine derartige Getriebeanordnung hervor. Die Getriebeanordnung umfasst ein hydrostatisches Getriebe, das mit einem mechanischen Getriebe gekoppelt ist, um einen ersten Fahrbereich und einen zweiten Fahrbereich auszuwählen. Eine Steuervorrichtung führt einen Schaltvorgang vom hierfür vorgesehenen ersten Getriebebereich zu dem zweiten Getriebebereich aus. Dieser Stand der Technik löst das Problem im Fahrbereich um den Stillstand des Fahrzeuges herum die gesamte Antriebsleistung nicht leistungsverzweigt zu wandeln, so dass ein Reversieren des Fahrzeuges rein hydrostatisch ohne Schaltung einer Kupplung im Stillstand erfolgen kann, und dass in diesem Fahrbereich, in welchem für die Fahrzeuge meist der Hauptarbeitsbereich liegt, keine Blindleistung im Hydraulikkreislauf auftritt. Eine Schaltung der Kupplungen soll nur beim Wechsel der Fahrbereiche und dann bei gleichen Drehzahlen der zu verbindenden Teile stattfinden.From DE 101 44 943 A1, such a transmission arrangement is apparent. The transmission assembly includes a hydrostatic transmission coupled to a mechanical transmission to select a first range of travel and a second range of travel. A control device carries out a switching operation from the first transmission region provided for this purpose to the second transmission region. This state of the art solves that Problem in the driving range to the standstill of the vehicle around the entire drive power not power split, so that reversing the vehicle purely hydrostatic can be done without switching a clutch at a standstill, and that in this driving range, in which for the vehicles usually the main working area, no reactive power in the hydraulic circuit occurs. A circuit of the clutches should take place only when changing the driving ranges and then at the same speeds of the parts to be joined.

Ein Nachteil dieses Standes der Technik besteht jedoch darin, dass das vorstehend dargelegte Ergebnis nur mit einem erheblichen bauteiletechnischen Aufwand umgesetzt wird. So sind eine Vielzahl von einzelnen Kupplungen innerhalb des Getriebes erforderlich, welche koordiniert durch eine zentrale elektronische Steuervorrichtung anzusteuern sind.A disadvantage of this prior art, however, is that the above result is implemented only with a considerable component-technical effort. Thus, a plurality of individual clutches are required within the transmission, which are coordinated by a central electronic control device to control.

Es ist daher die Aufgabe der vorliegenden Erfindung, eine Getriebeanordnung der vorstehend beschriebenen Art dahingehend weiterzuverbessern, dass ein breiter Fahrbereich der Getriebeanordnung unter Einsatz eines minimalen Bauteileaufwands möglich wird.It is therefore the object of the present invention to further improve a gear arrangement of the type described above in such a way that a broad driving range of the gear arrangement is made possible with the use of a minimal component expenditure.

Die Aufgabe wird ausgehend von einer Getriebeanordnung gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die nachfolgenden abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved on the basis of a gear arrangement according to the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give advantageous developments of the invention.

Die Erfindung schließt die technische Lehre ein, dass entsprechend eines ersten Fahrbereichs das Sonnenrad der einzigen Planetenstufe über eine erste Kupplung mit einem Hohlrad der Planetenstufe in Wirkverbindung steht, so dass die Abtriebsdrehzahl der Planetenstufe linear von der Abtriebsdrehzahl des hydrostatischen Getriebes abhängt, und dass ferner entsprechend eines zweiten Fahrbereiches das Hohlrad mit dem hydrostatischen Getriebe in Wirkverbindung steht, wobei gleichzeitig das Sonnenrad über eine zweite Kupplung mit einer Getriebeantriebswelle in Wirkverbindung steht, so dass sich die Drehzahlen von Hohlrad und Sonnenrad überlagern, und dass die erste Kupplung über eine Getriebestufe mit dem Hohlrad der Planetenstufe in Wirkverbindung steht, und dass das Hohlrad über eine Getriebestufe mit dem hydrostatischen Getriebe in Wirkverbindung steht, wobei mindestens eine Getriebestufe ein auf einer Welle starr angeordnetes Stirnrad besitzt und die Welle vom hydrostatischen Getriebe angetrieben ist, um im ersten Fahrbereich das Hohlrad und das Sonnenrad der Planetenstufe miteinander zu verbinden.The invention includes the technical teaching that corresponding to a first driving range, the sun gear of the single planetary stage via a first clutch with a ring gear of the planetary stage is in operative connection, so that the output speed of the planetary stage depends linearly on the output speed of the hydrostatic transmission, and that further accordingly a second driving range, the ring gear is in operative connection with the hydrostatic transmission, wherein at the same time the sun gear via a second clutch with a Transmission input shaft is in operative connection, so that superimpose the rotational speeds of the ring gear and sun gear, and that the first clutch via a gear stage with the ring gear of the planetary stage is in operative connection, and that the ring gear via a gear stage with the hydrostatic transmission is in operative connection, wherein at least a gear stage has a spur gear rigidly mounted on a shaft and the shaft is driven by the hydrostatic transmission to connect the ring gear and the sun gear of the planetary gear stage in the first driving range.

Der Vorteil der erfindungsgemäßen Getriebeanordnung besteht insbesondere darin, dass hiermit ein hohes Übersetzungsverhältnis durch Wechsel der Betriebsweise über zwei Kupplungen möglich ist, wodurch zwei sich einander ergänzende Fahrbereiche für die Vorwärtsfahrt eines Fahrzeuges zur Verfügung gestellt werden. Unter Hinzufügung einer weiteren Kupplung können auch zwei Fahrbereiche für die Rückwärtsfahrt des Fahrzeuges bereitgestellt werden. Der recht geringe Aufwand von mechanischen Bauteilen resultiert daraus, dass nur eine Planetenstufe als Überlagerungsstufe eingesetzt wird. Im ersten Fahrbereich werden das Hohlrad und das Sonnenrad der Planetenstufe über die Kupplung miteinander verbunden. Der Antrieb erfolgt dabei ausgehend von der Getriebeeingangswelle über das hydrostatische Getriebe in die Planetenstufe, deren Planetensteg den Abtrieb bildet. Im zweiten Fahrbereich erfolgt der Antrieb leistungsverzweigt zum Einen direkt mechanisch über die zweite Kupplung auf das Sonnenrad der Planetenstufe und zum Anderen auch über das hydrostatische Getriebe auf das Hohlrad der Planetenstufe. Der Abtrieb erfolgt weiterhin über den Planetensteg. Die erste Kupplung ist in diesem Fall geöffnet.The advantage of the gear arrangement according to the invention is in particular that hereby a high transmission ratio is possible by changing the mode of operation via two clutches, whereby two complementary driving ranges are provided for the forward travel of a vehicle. With the addition of a further clutch, two driving ranges for the reverse travel of the vehicle can be provided. The relatively low cost of mechanical components results from the fact that only one planetary stage is used as an overlay stage. In the first driving range, the ring gear and the sun gear of the planetary stage are connected to each other via the clutch. The drive takes place starting from the transmission input shaft via the hydrostatic transmission in the planetary stage, the planetary web forms the output. In the second driving range, the drive is power-split on the one hand directly mechanically via the second clutch to the sun gear of the planetary stage and on the other hand via the hydrostatic transmission to the ring gear of the planetary stage. The output continues via the planet web. The first clutch is open in this case.

Vorzugsweise ist vorgesehen, dass beide Getriebestufen je ein auf einer gemeinsamen Welle starr angeordnetes Stirnrad besitzen, und dass die Welle vom hydrostatischen Getriebe angetrieben ist. Hierdurch ergibt sich eine besonders bauteilsparende Anordnung.It is preferably provided that both gear stages each have a rigidly arranged on a common shaft spur gear, and that the shaft is driven by the hydrostatic transmission. This results in a particularly component-saving arrangement.

Alternativ hierzu kann auch nur die Getriebestufe ein auf einer Welle starr angeordnetes Stirnrad besitzen und die Welle vom hydrostatischen Getriebe angetrieben sein, wobei besagtes Stirnrad mit einem außenverzahnten Hohlrad der nachgeschalteten Getriebestufe kämmt. Durch diese Ausführungsform lässt sich ein noch kompakterer Aufbau erzielen, da die Leistung nicht über eine extra Stirnradstufe zu laufen hat, sondern über parallele Leistungspfade, die durch die Anzahl der Planetenräder gegeben sind.Alternatively, only the gear stage may have a spur gear rigidly mounted on a shaft, and the shaft may be driven by the hydrostatic transmission, said spur gear meshing with an externally toothed ring gear of the downstream gear stage. By this embodiment, an even more compact design can be achieved because the power does not have to run through an extra spur gear, but over parallel power paths, which are given by the number of planetary gears.

Vorteilhafterweise erfolgt die Umschaltung zwischen dem ersten Fahrbereich und dem zweiten Fahrbereich durch ein wechselseitiges Betätigen der beiden Kupplungen über eine zentrale Steuereinheit, welche zugleich auch das hydrostatische Getriebe nach Maßgabe des Fahrwunsches ansteuert.Advantageously, the switching between the first driving range and the second driving range is effected by a mutual actuation of the two clutches via a central control unit, which at the same time also controls the hydrostatic transmission in accordance with the driving intention.

Die erfindungsgemäße Getriebeanordnung kann zum Zwecke einer Drehzahlanpassung verschiedene Getriebestufen enthalten. So treibt die Getriebeeintriebswelle das hydrostatische Getriebe vorzugsweise über eine zwischengeschaltete Getriebestufe an. Des Weiteren kann die erste Kupplung über eine weitere Getriebestufe mit dem Hohlrad der Planetenstufe in Wirkverbindung stehen, also indirekt. Ferner kann es aber auch von Vorteil sein, wenn auch das Hohlrad über eine zwischengeschaltete Getriebestufe mit dem hydrostatischen Getriebe in Wirkverbindung steht.The gear arrangement according to the invention may contain different gear stages for the purpose of speed adaptation. Thus, the transmission input shaft drives the hydrostatic transmission preferably via an intermediate gear stage. Furthermore, the first clutch can be in operative connection with the ring gear of the planetary stage via an additional gear stage, ie indirectly. Furthermore, it may also be advantageous if the ring gear is also operatively connected to the hydrostatic transmission via an intermediate gear stage.

Gemäß einer weiteren die Erfindung verbessernden Maßnahme ist vorgesehen, dass zwischen der Getriebeeintriebswelle und dem Sonnenrad der Planetenstufe mindestens eine weiteren zusätzliche Kupplung angeordnet ist, um auch im Rückwärtslauf mindestens einen zweiten Fahrbereich zu ermöglichen. Vorzugsweise steht auch diese zusätzliche Kupplung über eine zugeordnete Getriebestufe mit einem drehrichtungsändernden Zwischenrad mit der Getriebeeintriebswelle in Wirkverbindung.According to a further measure improving the invention, it is provided that at least one further additional clutch is arranged between the transmission input shaft and the sun gear of the planetary stage in order to enable at least one second driving range even in reverse. Preferably, this additional clutch is also operatively connected to the transmission input shaft via an associated gear stage having a direction-changing intermediate gear.

Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt:

Fig.1
ein Schaltbild einer Getriebeanordnung mit Getriebemitteln zur Drehzahlüberlagerung in einer ersten Ausführungsform,
Fig.2
ein Schaltbild einer Getriebeanordnung mit Getriebemitteln zur Drehzahlüberlagerung in einer zweiten Ausführungsform, und
Fig.3
ein Schaltbild einer Getriebeanordnung mit Getriebemitteln zur Drehzahlüberlagerung in einer dritten Ausführungsform.
Further measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to FIGS. It shows:
Fig.1
a circuit diagram of a transmission arrangement with transmission means for speed superposition in a first embodiment,
Fig.2
a circuit diagram of a transmission arrangement with transmission means for speed superposition in a second embodiment, and
Figure 3
a circuit diagram of a transmission arrangement with transmission means for speed superposition in a third embodiment.

Gemäß Fig.1 besteht die Getriebeanordnung dem Kraftfluss folgend aus einer eingangsseitigen Getriebeeintriebswelle 1, welche durch einen - nicht weiter dargestellten - Motor angetrieben wird. Der Getriebeeintriebswelle 1 ist ein hydrostatisches Getriebe 2 nachgeschaltet. Das hydrostatische Getriebe 2 besteht aus einer verstellbaren Hydraulikpumpe 2a, die mit einem verstellbaren Hydraulikmotor 2b hydrostatisch gekoppelt ist. Ausgangsseitig des hydrostatischen Getriebes 2 ist eine Planetenstufe 3 angekoppelt. Entlang eines von der Getriebeeintriebswelle 1 über einer Getriebestufe 10 und einer fortführenden Welle 6 verlaufenden parallelen Kraftfluss sind zwei in Reihe zueinander geschalteter Kupplungen 4 und 5 vorgesehen. Die endseitige Kupplung 4 steht mit dem Sonnenrad 3b der Planetenstufe 3 in Verbindung. Der Planetenträger 3c der Planetenstufe 3 bildet den Abtrieb der Getriebeanordnung.According to FIG. 1, the gear arrangement follows the force flow from an input-side gear input shaft 1, which is driven by a motor (not shown). The transmission input shaft 1 is connected downstream of a hydrostatic transmission 2. The hydrostatic transmission 2 consists of an adjustable hydraulic pump 2 a, which is hydrostatically coupled to an adjustable hydraulic motor 2 b. On the output side of the hydrostatic transmission 2, a planetary stage 3 is coupled. Along one of the transmission input shaft 1 via a gear stage 10 and a continuing wave 6 parallel flow of power two series-connected couplings 4 and 5 are provided. The end coupling 4 is in communication with the sun gear 3b of the planetary stage 3. The planet carrier 3c of the planetary stage 3 forms the output of the gear assembly.

Der Kraftfluss geht in einem ersten Fahrbereich von der Getriebeeintriebeswelle 1 über eine eingangsseitige Getriebestufe 7 auf die Antriebswelle der Verstellpumpe 2a des hydrostatischen Getriebes 2. Die Abtriebswelle des hydrostatischen Motors 2b des hydrostatischen Getriebes 2 steht über nachgeschaltete Getriebestufen 8 und 9 in Wirkverbindung mit dem Hohlrad 3a der Planetenstufe 3 sowie auch mit der Kupplung 4 des parallelen Kraftflusses. Durch Schließen der Kupplung 4 werden im ersten Fahrbereich Hohlrad 3a und Sonnenrad 3b der Planetenstufe 3 über die Getriebestufen 8 und 9 zusätzlich miteinander verbunden, wodurch die Anzahl der Freiheitsgrade der Planetenstufe 3 reduziert wird, so dass die Abtriebsdrehzahl des Planetensteges 3c direkt von der Abtriebsdrehzahl des Hydraulikmotors 2b abhängt.The power flow is in a first driving range of the transmission input shaft 1 via an input side gear 7 on the drive shaft of the variable displacement 2a of the hydrostatic transmission 2. The output shaft of the hydrostatic motor 2b of the hydrostatic transmission 2 is connected via downstream gear stages 8 and 9 in operative connection with the ring gear 3a the planetary stage 3 and also with the clutch 4 of the parallel power flow. By closing the clutch 4 in the first driving range ring gear 3a and 3b of the planetary planetary gear 3 via the gear stages 8 and 9 are additionally interconnected, whereby the number of degrees of freedom of the planetary stage 3 is reduced so that the output speed of the planetary gear 3c directly from the output speed of Hydraulic motor 2b depends.

Wird nun bei konstanter Antriebsdrehzahl die verstellbare Hydraulikpumpe 2a aus der Nullstellung auf größeres Fördervolumen ausgeschwenkt, erhöht sich proportional zu dem ansteigenden Fördervolumen auch die Drehzahl am Hydraulikmotor 2b und damit die Abtriebsdrehzahl des hydrostatischen Getriebes 2. Ein Verschwenken der Verstellpumpe 2a in die entgegengesetzte Richtung bedeutet eine andere Drehrichtung am Hydraulikmotor 2b und damit eine Rückwärtsfahrt des Fahrzeuges.If the adjustable hydraulic pump 2a is now swung out of the zero position to a larger delivery volume at a constant input speed, the rotational speed at the hydraulic motor 2b and thus the output speed of the hydrostatic transmission 2 increases in proportion to the increasing delivery volume. Pivoting the variable displacement pump 2a in the opposite direction means another direction of rotation on the hydraulic motor 2b and thus a reverse drive of the vehicle.

Die Übersetzungen der Getriebestufen 7 bis 10 sowie der Planetenstufe 3 sind derart aufeinander abgestimmt, dass bei maximaler Drehzahl des verstellbaren Hydraulikmotors 2b das Sonnenrad 3b und die Welle 6 des parallelen Kraftflusses die gleiche Drehzahl aufweist. In diesem Betriebspunkt wird mittels einer - hier nicht weiter dargestellten - Steuereinheit die erste Kupplung 4 geöffnet und die zweite Kupplung 5 geschlossen. Demzufolge dreht das Sonnenrad 3b der Planetenstufe 3 mit konstanter Drehzahl gleichsinnig mit dem Planetensteg 3c während das Hohlrad 3a mit maximaler Drehzahl entgegengesetzt rotiert. Wird nun durch Veränderung der Übersetzung des hydrostatischen Getriebes 2 durch entsprechende Ansteuerung über die Steuereinheit das Hohlrad 3a erst verzögert und dann in entgegengesetzte Richtung beschleunigt, so ergibt sich durch eine Drehzahlüberlagerung ein weiteres Beschleunigen des Planetensteges 3c, was dem zweiten Fahrbereich entspricht.The ratios of the gear stages 7 to 10 and the planetary stage 3 are coordinated such that at maximum speed of the variable hydraulic motor 2b, the sun gear 3b and the shaft 6 of the parallel power flow has the same speed. In this operating point, the first clutch 4 is opened and the second clutch 5 is closed by means of a - not shown here - control unit. Accordingly, the sun gear 3b of the planetary stage 3 rotates in a constant speed in the same direction as the planetary gear 3c while the ring gear 3a rotates at the maximum rotational speed in the opposite direction. Is now delayed by changing the ratio of the hydrostatic transmission 2 by appropriate control via the control unit, the ring gear 3a and then in Accelerated opposite direction, it follows by a speed superposition further acceleration of the planetary land 3c, which corresponds to the second driving range.

Gemäß Fig.2 ist zusätzlich zu der vorstehend beschriebenen Ausführungsform neben der Getriebestufe 10 mit Kupplung 5 eine weitere Kupplung 5b mit zugeordneter Getriebestufe 10b eingeführt. Die Getriebestufe 10b enthält ein Zwischenrad 11 zur Änderung der Drehrichtung. Über diese zusätzlichen Bestandteile der Getriebeanordnung kann auch für die Rückwärtsfahrt über eine entsprechende Ansteuerung durch die Steuereinheit ein zweiter Fahrbereich dargestellt werden.According to Figure 2, in addition to the embodiment described above, in addition to the gear stage 10 with clutch 5, a further clutch 5b is introduced with associated gear stage 10b. The gear stage 10b includes an intermediate gear 11 for changing the direction of rotation. By means of these additional components of the gear arrangement, a second driving range can also be represented for the reverse drive via a corresponding control by the control unit.

Gemäß Fig.3 besitzt - im Unterschied zum erstgenannten Ausführungsbeispiel - nur die als Stirnradgetriebe ausgebildete Getriebestufe 8 ein auf der Welle starr angeordnetes Stirnrad, das vom hydr660+160ostatischen Getriebe 2 angetrieben ist. Das besagte Stirnrad kämmt wiederum mit einem außenverzahnten Hohlrad 9a der nachgeschalteten Getriebestufe 9, die hier ein Planetengetriebe ist. Die Kupplung 4 dient dem Fixieren des Planetenstegs 9c von Getriebestufe 9. Die Sonnenräder 3b und 9b der Getriebestufen 3 bzw. 9 sind auf einer gemeinsamen Welle angeordnet, die mit der Kupplung 5 fixierbar ist. Die der Getriebestufe 9 nachgeschaltete Planetenstufe 3 wird auch über ein gemeinsames Hohlrad 9a und 3a angetrieben. Der Abtrieb bei der Planetenstufe 3 erfolgt ebenfalls über den Planetensteg 3c.According to Figure 3 has - in contrast to the former embodiment - only designed as a spur gear 8 a gear on the shaft rigidly arranged spur gear, which is driven by the hydr660 + 160ostatic transmission 2. The said spur gear in turn meshes with an externally toothed ring gear 9a of the downstream gear stage 9, which is here a planetary gear. The clutch 4 is used to fix the planetary land 9c of gear stage 9. The sun gears 3b and 9b of the gear stages 3 and 9 are arranged on a common shaft which is fixable with the clutch 5. The gear stage 9 downstream planetary stage 3 is also driven by a common ring gear 9a and 3a. The output at the planetary stage 3 also takes place via the planetary land 3c.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
GetriebeeintriebswelleGearbox input shaft
22
hydrostatisches Getriebehydrostatic transmission
33
Planetenstufeplanetary stage
3a3a
Hohlradring gear
3b3b
Sonnenradsun
3c3c
Planetenstegplanet spider
44
erste Kupplungfirst clutch
55
zweite Kupplungsecond clutch
66
Wellewave
77
Getriebestufegear stage
88th
Getriebestufegear stage
99
Getriebestufegear stage
1010
Getriebestufegear stage
1111
Zwischenradidler

Claims (9)

Getriebeanordnung, insbesondere für einen Antrieb eines Fahrzeuges, mit einem hydrostatischen Getriebe (2), dem mindestens eine Planetenstufe (3) nachgeschaltet ist, wobei die Ankopplung der Planetenstufe (3) an das hydrostatische Getriebe (2) über zwischengeschaltete Getriebemittel zur Drehzahlüberlagerung innerhalb der Planetenstufe (3) erfolgt, indem entsprechend eines ersten Fahrbereichs das Sonnenrad (3b) der einzigen Planetenstufe (3) über eine erste Kupplung (4) mit einem Hohlrad (3a) der Planetenstufe (3) in Wirkverbindung steht, so dass die Abtriebsdrehzahl der Planetenstufe (3) linear von der Abtriebsdrehzahl des hydrostatischen Getriebes (2) abhängt, und dass entsprechend eines zweiten Fahrbereichs das Hohlrad (3a) mit dem hydrostatischen Getriebe (2) in Wirkverbindung steht,
dadurch gekennzeichnet, dass gleichzeitig das Sonnenrad (3b) über eine zweite Kupplung (5) mit einer Getriebeeintriebswelle (1) in Wirkverbindung steht, so dass sich infolge Leistungsverzweigung die Drehzahlen von Hohlrad (3a) und Sonnenrad (3b) überlagern,
und dass die erste Kupplung (4) über eine Getriebestufe (9) mit dem Hohlrad (3a) der Planetenstufe (3) in Wirkverbindung steht,
und dass das Hohlrad (3a) über eine Getriebestufe (8) mit dem hydrostatischen Getriebe (2) in Wirkverbindung steht,
wobei mindestens eine Getriebestufe (8) ein auf einer Welle starr angeordnetes Stirnrad besitzt und die Welle vom hydrostatischen Getriebe (2) angetrieben ist, um im ersten Fahrbereich das Hohlrad (3a) und das Sonnenrad (3b) der Planetenstufe (3) miteinander zu verbinden.Transmission arrangement, in particular for a drive of a vehicle, with a hydrostatic transmission (2), the at least one planetary stage (3) is connected, wherein the coupling of the planetary stage (3) to the hydrostatic transmission (2) via intermediate transmission means for speed superposition within the planetary stage (3) takes place in accordance with a first driving range, the sun gear (3b) of the single planetary stage (3) via a first clutch (4) with a ring gear (3a) of the planetary stage (3) is in operative connection, so that the output speed of the planetary stage ( 3) depends linearly on the output speed of the hydrostatic transmission (2), and that according to a second driving range the ring gear (3a) is in operative connection with the hydrostatic transmission (2),
characterized in that at the same time the sun gear (3b) via a second clutch (5) with a transmission input shaft (1) is in operative connection, so that overlap due to power branching the speeds of ring gear (3a) and sun gear (3b),
and that the first clutch (4) via a gear stage (9) with the ring gear (3a) of the planetary stage (3) is in operative connection,
and that the ring gear (3a) via a gear stage (8) with the hydrostatic transmission (2) is in operative connection,
wherein at least one gear stage (8) has a rigidly arranged on a shaft spur gear and the shaft of the hydrostatic transmission (2) is driven to connect the ring gear (3a) and the sun gear (3b) of the planetary stage (3) in the first driving range with each other , Getriebeanordnung nach Anspruch 1,
dadurch gekennzeichnet, dass beide Getriebestufen (8 und 9) je ein auf einer gemeinsamen Welle starr angeordnetes Stirnrad besitzen, und dass die Welle vom hydrostatischen Getriebe (2) angetrieben ist (Fig. 1 und 2).Gear arrangement according to claim 1,
characterized in that both gear stages (8 and 9) each have a rigidly arranged on a common shaft spur gear, and that the shaft of the hydrostatic transmission (2) is driven (Fig. 1 and 2). Getriebeanordnung nach Anspruch 1,
dadurch gekennzeichnet, dass nur die Getriebestufe (8) ein auf einer Welle starr angeordnetes Stirnrad besitzt und die Welle vom hydrostatischen Getriebe (2) angetrieben ist,
wobei besagtes Stirnrad mit einem außenverzahnten Hohlrad (9a) der nachgeschalteten Getriebestufe (9) kämmt (Fig. 3).Gear arrangement according to claim 1,
characterized in that only the gear stage (8) has a spur gear rigidly mounted on a shaft and the shaft is driven by the hydrostatic transmission (2),
wherein said spur gear meshes with an externally toothed ring gear (9a) of the downstream gear stage (9) (Fig. 3). Getriebeanordnung nach Anspruch 1,
dadurch gekennzeichnet, dass die Umschaltung zwischen dem ersten Fahrbereich und dem zweiten Fahrbereich durch wechselseitiges Betätigen der Kupplungen (4 und 5) über eine zentrale Steuereinheit erfolgt, welche zugleich auch das hydrostatische Getriebe (2) nach Maßgabe des Fahrwunsches ansteuert.Gear arrangement according to claim 1,
characterized in that the switching between the first driving range and the second driving range by alternately pressing the clutches (4 and 5) via a central control unit, which at the same time also controls the hydrostatic transmission (2) in accordance with the driving desire. Getriebeanordnung nach Anspruch 1,
dadurch gekennzeichnet, dass die Getriebeeintriebswelle (1) über eine Getriebestufe (7) das hydrostatische Getriebe (2) antreibt.Gear arrangement according to claim 1,
characterized in that the transmission input shaft (1) via a gear stage (7) drives the hydrostatic transmission (2). Getriebeanordnung nach Anspruch 1,
dadurch gekennzeichnet, dass die zweite Kupplung (5) über eine Getriebestufe (10) mit der Getriebeeintriebswelle (1) in Wirkverbindung steht.Gear arrangement according to claim 1,
characterized in that the second clutch (5) via a gear stage (10) with the transmission input shaft (1) is in operative connection. Getriebeanordnung nach Anspruch 1,
dadurch gekennzeichnet, dass das hydrostatische Getriebe (2) aus einer verstellbaren Hydraulikpumpe (2a) besteht, die mit einem verstellbaren Hydraulikmotor (2b) hydrostatisch gekoppelt ist.Gear arrangement according to claim 1,
characterized in that the hydrostatic transmission (2) consists of an adjustable hydraulic pump (2a) which is hydrostatically coupled to an adjustable hydraulic motor (2b). Getriebeanordnung nach einem der vorstehenden Ansprüche,
dadurch gekennzeichnet, dass zwischen der Getriebeeintriebswelle (1) und dem Sonnenrad (3b) der Planetenstufe (3) mindestens eine zusätzliche Kupplung (5b) angeordnet ist, um auch im Rückwärtslauf mindestens einen zweiten Fahrbereich zu ermöglichen (Fig. 2).Gear arrangement according to one of the preceding claims,
characterized in that between the transmission input shaft (1) and the sun gear (3b) of the planetary stage (3) at least one additional clutch (5b) is arranged to allow at least a second driving range even in reverse (Figure 2). Getriebeanordnung nach Anspruch 1,
dadurch gekennzeichnet, dass die zusätzliche Kupplung (5b) über eine zugeordnete Getriebestufe (10b) mit einem drehrichtungsändernden Zwischenrad (11) mit der Getriebeeintriebswelle (1) in Wirkverbindung steht.Gear arrangement according to claim 1,
characterized in that the additional clutch (5b) via an associated gear stage (10b) with a direction of rotation changing intermediate wheel (11) with the transmission input shaft (1) is in operative connection.
EP05110321A 2004-11-04 2005-11-03 Power-split hydromechanical transmission with summing transmission means Not-in-force EP1655515B1 (en)

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PL06121775T PL1734286T3 (en) 2004-11-04 2005-11-03 Power-splitting hydromechanical transmission with superimposing transmission means

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DE102004053254A DE102004053254B3 (en) 2004-11-04 2004-11-04 Gear arrangement with gear means for speed superposition

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WO2014095317A1 (en) * 2012-12-17 2014-06-26 Linde Hydraulics Gmbh & Co. Kg Power-split gearbox with different operating states

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DE502005000398D1 (en) 2007-04-05
EP1734286A2 (en) 2006-12-20
CN1769741A (en) 2006-05-10
CN1769741B (en) 2010-05-12
PL1734286T3 (en) 2010-03-31
EP1655515B1 (en) 2007-02-21
EP1734286A3 (en) 2007-09-19
DE502005007987D1 (en) 2009-10-08
ATE441049T1 (en) 2009-09-15
US7381144B2 (en) 2008-06-03
DE102004053254B3 (en) 2006-06-01
EP1734286B1 (en) 2009-08-26
US20060094553A1 (en) 2006-05-04
ATE354747T1 (en) 2007-03-15

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